Mobile work machine, drive system and connection method

Abstract

The invention relates to a mobile working machine, in particular a mobile crane, comprising a movable undercarriage, a superstructure rotatably mounted on the undercarriage about a superstructure pivot axis and detachably connected to the undercarriage via a coupling device, and a mechanical power transmission means, wherein the undercarriage comprises a motor and a first shaft mechanically driven by the motor, which is mechanically connected to a second shaft of the superstructure via the power transmission means. According to the invention, the working machine comprises a support arrangement on which the power transmission means is mounted and which includes first and second connecting elements by means of which the power transmission means can be rigidly connected to the undercarriage in a transport state in which the superstructure is separated from the undercarriage, and rigidly connected to the superstructure in a working state in which the superstructure is rotatably mounted on the undercarriage.Furthermore, the power transmission means is detachably connected to the second shaft via a mechanical interface in the operating state. The invention further relates to a drive system for a working machine according to the invention and to a method for connecting the undercarriage and superstructure of such a working machine.

Description

[0001] The present invention relates to a mobile work machine, in particular a mobile crane, according to the preamble of claim 1, a drive system and a method for connecting the superstructure and undercarriage of such a work machine.

[0002] Mobile work machines often have a movable undercarriage and a rotating superstructure mounted on it, such as rail cranes, crawler cranes, or mobile cranes. The latter are typically movable on public roads and have a wheeled chassis, for which certain maximum axle loads for public road traffic must be taken into account depending on the country. For example, in Germany, mobile cranes are permitted to travel with a maximum load of 12 t per axle. This limits the mass that can be used to increase the load capacity of such mobile cranes.

[0003] One way to increase the maximum lifting capacity of mobile cranes is to dismantle certain components for travel on public roads. This, however, increases the effort required to prepare the mobile crane for operation. However, this effort is offset by the higher achievable lifting capacity, so this effort can be justified in certain cases. Components that can be dismantled are the uppercarriage and the boom, which on most mobile cranes is designed as a telescopic boom. These components can be transported to the site as separate transport units despite their large mass. The mobile crane can travel to the site on public roads with its undercarriage alone. These considerations regarding dismantled and separately transportable components apply not only to mobile cranes, but also to other mobile work machines that can be dismantled into separate transport units.

[0004] Larger mobile cranes typically have two engines: a lower carriage engine in the undercarriage and a superstructure engine in the uppercarriage. The lower carriage engine typically powers the entire crane, while the superstructure engine typically drives hydraulic motors via a pump distribution gearbox. These motors perform the usual crane functions (boom luffing, superstructure rotation, operating cable winches, etc.).

[0005] Single-engine mobile cranes are also known, which have only one engine in the undercarriage. By eliminating the superstructure engine and its weight, this weight can be invested in the crane's lifting capacity and / or the stability of various components. The superstructure's consumers must therefore be supplied from the undercarriage. A so-called "hydraulic shaft" is often used for this purpose. This involves a rotary union between the undercarriage and superstructure that feeds hydraulic oil into the supercarriage, which directly or indirectly supplies the respective crane actuators. However, these hydraulic shafts are not only complex in design, but also make it difficult to disassemble the supercarriage from the undercarriage for transport.

[0006] Alternatively, a mechanical linkage, driven by the undercarriage engine, can be routed into the superstructure via the rotary union to drive a pump distribution gearbox, for example. However, such solutions have so far only been used for smaller mobile cranes where the superstructure is not dismantled for transport, as separating the mechanical linkage would be too complex with previous solutions.

[0007] DE 10 2011 108 893 A1 already discloses an upper carriage mounted on a rotatable undercarriage. A mechanical shaft driven by the undercarriage engine is mechanically connected to a second shaft of the upper carriage via a gearbox.

[0008] Against this background, the object of the present invention is to provide a generic mobile work machine whose upper carriage can be quickly and easily separated from the undercarriage for transport or connected to the undercarriage for preparation in the working state.

[0009] According to the invention, this object is achieved by a work machine having the features of claim 1, by a drive system having the features of claim 14, and by a method having the features of claim 15. Advantageous embodiments of the invention emerge from the subclaims and the following description.

[0010] Accordingly, a mobile work machine, in particular a mobile crane, is proposed, comprising a movable undercarriage, an uppercarriage mounted on the undercarriage for rotation about a particularly vertical uppercarriage axis of rotation, and a mechanical power transmission device. The uppercarriage is detachably connected to the undercarriage via a coupling device, allowing it to be removed from the undercarriage for separate transport of the undercarriage and uppercarriage. In this case, the detachable connection between the uppercarriage and undercarriage refers to a connection designed for the regular removal and installation of the uppercarriage.

[0011] This separation can be performed frequently and without significant wear, which is especially not the case for separation at the expansion bolts of a roller slewing ring, since these bolts would have to be replaced after only a few separation operations at the latest. Consequently, the aforementioned separable connection between the uppercarriage and the undercarriage does not involve separation at the conventionally provided expansion bolts of a roller slewing ring. Instead, the work machine according to the invention preferably comprises a quick-coupling device for separating the uppercarriage and the undercarriage, in order to enable the assembly and disassembly of the uppercarriage to be carried out quickly and easily. The quick-coupling device can comprise a bolt connection.

[0012] In this case, a screw connection is not understood as a quick coupling or quick coupling device.

[0013] The undercarriage comprises an engine and a first shaft mechanically driven by the engine. The uppercarriage comprises a second shaft, which in particular drives one or more consumers of the uppercarriage, for example a pump distribution gear. The second shaft is mechanically connected or connectable to the first shaft via the power transmission mechanism. The undercarriage engine thus mechanically drives the second shaft via the first shaft and the power transmission mechanism. This eliminates the need for a separate uppercarriage engine, which saves weight and costs due to current environmental regulations. The power is transferred from the undercarriage to the uppercarriage mechanically and not hydraulically, thus eliminating the need for a complicated and leak-prone "hydraulic shaft."

[0014] According to the invention, the work machine comprises a support arrangement on which the power transmission means is mounted. The support arrangement and thus the power transmission means are not permanently connected to the undercarriage (or the superstructure), but can be selectively connected to the undercarriage or the superstructure. For this purpose, the support arrangement comprises at least one first connecting element, preferably a plurality of first connecting elements, via which the support arrangement and thus the power transmission means can be connected to the undercarriage in a rotationally rigid or immovable manner in a transport state in which the superstructure is separated from the undercarriage and is moved separately, for example. This can prevent, for example, the power transmission means from unintentionally rotating when the undercarriage is moved. As a result, the power transmission means as a whole, with its support arrangement, can be moved safely in road traffic.

[0015] Furthermore, the support arrangement comprises at least one second connecting element, preferably a plurality of second connecting elements, via which the support arrangement and thus the power transmission means can be connected to the superstructure in a rotationally rigid or immovable manner in a working state in which the superstructure is rotatably mounted on the undercarriage and can therefore perform the usual working functions. As a result, the power transmission means rotates with the superstructure when the superstructure rotates relative to the undercarriage. In this state, the power transmission means is connected to the undercarriage in particular only via the first shaft and a possibly present driver and can therefore rotate relative to the undercarriage. As a result, the mechanical power transmission from the undercarriage to the superstructure takes place independently of the rotational position of the superstructure relative to the undercarriage.

[0016] According to the invention, the work machine further comprises a mechanical interface via which the power transmission means is detachably connected to the second shaft in the working state. In order to dismantle the uppercarriage from the undercarriage, the second shaft must be separated from the power transmission means. This can be done quickly and easily via the mechanical interface provided specifically for this purpose, which can preferably comprise a quick-release coupling. The separation between the undercarriage and uppercarriage thus occurs at the aforementioned mechanical interface between the power transmission means and the second shaft (and in particular at a slewing ring between the undercarriage and uppercarriage).

[0017] The solution according to the invention enables a mechanical energy or power transmission from the undercarriage to the superstructure regardless of the size of the working machine and thus in particular a single-engine drive for devices (e.g. large mobile cranes) in which the superstructure is regularly dismantled for transport.

[0018] The support arrangement can preferably be arranged on the upper side of the undercarriage, so that a connection to the superstructure or to the second shaft can be easily established. In particular, the power transmission means can be located in the area of ​​a slewing ring between the superstructure and undercarriage. The undercarriage can have a wheeled chassis, although other chassis, such as a rail chassis or a crawler chassis, are also conceivable.

[0019] When referring to first connecting elements or second connecting elements in the plural, unless otherwise specified, this always refers to at least one first or second connecting element. However, a preferred embodiment is one in which several first and several second connecting elements are provided, e.g., three or four of these elements each.

[0020] When we speak of a rotationally rigid connection in this case, we mean in particular an immobile connection, ie no translational degrees of freedom are provided.

[0021] The connection between the support arrangement and the undercarriage via the first connecting elements can be referred to as the first connection and the connection between the support arrangement and the uppercarriage via the second connecting elements can be referred to as the second connection. In particular, the first and second connections are only established simultaneously in an intermediate stage during the removal or installation of the uppercarriage. In the working state, in which the uppercarriage can be rotated together with the power transmission means relative to the undercarriage, only the second connection is active or established, while the first connection is disconnected. In the transport state, in contrast, only the first connection is established, while the second connection is disconnected (since the uppercarriage is not connected to the undercarriage). At any given time, however, one of the two connections is in particular established.

[0022] In one possible embodiment, the power transmission means is or comprises an angular gear. The angular gear laterally deflects the mechanical linkage running between the undercarriage and the upper carriage and, in an optional embodiment, can additionally have a fixed or adjustable torque transmission. The angular gear preferably comprises a first mechanical interface and a second mechanical interface, via which the angular gear is or can be mechanically detachably connected to the first shaft and connected to the second shaft. In addition to the second mechanical interface, via which the second shaft can be quickly and easily separated from the power transmission means, a first mechanical interface can also be provided in order to be able to quickly and easily separate the first shaft from the power transmission means or connect it to it.

[0023] In another possible embodiment, the coupling device comprises a rotary joint. This is preferably designed as a rolling bearing, in particular a large-diameter rolling bearing. The superstructure preferably has a rotary drive for actively rotating the superstructure via the rotary joint, which can be hydraulic, for example.

[0024] The second slewing ring preferably comprises a first slewing ring part connected to the undercarriage and a second slewing ring part connected to the superstructure, which are detachably connected to one another via a quick-coupling device (“quick connection”). This allows the superstructure to be separated from or connected to the undercarriage relatively quickly and easily, e.g. in order to transport the undercarriage and superstructure as separate transport units. The quick-coupling device can be based on a type of tongue and groove connection between the aforementioned slewing ring parts, which can be detachably locked to one another by means of several bolts. However, different solutions are conceivable here, which allow quick and easy mechanical assembly or disassembly of the superstructure and are designed for this purpose.

[0025] In a further possible embodiment, the power transmission means or the support arrangement is arranged within the aforementioned rotary joint. Preferably, in the working state, the uppercarriage is rotatably connected to the undercarriage only via the rotary joint of the coupling device, i.e., in particular, no further rotary joint is provided. This does not preclude the uppercarriage from being coupled or connected to the undercarriage via the first shaft and a possibly present driver.

[0026] In a further possible embodiment, the support arrangement comprises a console having the first and second connecting elements, wherein the force transmission means is preferably connected to the console via at least one damping element of the support arrangement. The support arrangement preferably comprises an arrangement of several damping elements. The force transmission means can be mounted on a holder, which in turn is connected to the console via the at least one damping element. The force transmission means is connected to the undercarriage in a vibration-damped manner via the at least one damping element.

[0027] The at least one damping element can be an elastic component such as a spring or an elastomer bearing. The at least one damping element compensates for vibrations or relative movements between the undercarriage and upper carriage, thereby protecting the mechanical drive system between the undercarriage and upper carriage. The support arrangement preferably comprises an arrangement of several damping elements symmetrical to a rotation axis of the power transmission means (which in particular coincides with the upper carriage rotation axis). An arrangement of four damping elements forming the corners of a rectangle or square is preferred, although other arrangements with fewer (e.g., three) or more than four damping elements are also possible.

[0028] In a further possible embodiment, the support arrangement comprises at least a first connecting element with a holding element, wherein the holding element can be fixed or locked in at least two positions via a first locking means. The holding element in turn comprises a first locking element which can be brought into engagement with a second locking element arranged on the undercarriage in order to connect the support arrangement to the undercarriage in a rotationally rigid or immovable manner. The first connecting element and the second locking element can preferably form a quick coupling which is designed to carry out the locking and unlocking between the support arrangement and the undercarriage regularly and quickly and easily. The support arrangement preferably comprises at least three first connecting elements and the undercarriage at least three second locking elements.

[0029] Two defined positions can be provided in which the retaining element can be locked. For example, the retaining element can have corresponding recesses into which a projection or pin of the first locking means engages.

[0030] The holding element can be designed to be adjustable in length so that manufacturing tolerances of the undercarriage can be compensated and the second connecting elements can be aligned.

[0031] In a further possible embodiment, the holding element is adjustable relative to the force transmission means along a longitudinal axis, in particular running parallel to the uppercarriage rotation axis, and can be locked in at least two different longitudinal positions (i.e., positions along the longitudinal axis) via the first locking means. As a result, the holding element can be "retracted" after the support assembly has been connected to the uppercarriage, i.e., moved away from the undercarriage, so that the support assembly can rotate with the uppercarriage without colliding with the undercarriage.

[0032] Preferably, the holding element is movable by rotation about its longitudinal axis between a locking position, in which the holding element and the second locking element are locked together, and an unlocking position, in which movement of the holding element relative to the carrier arrangement in the longitudinal direction is permitted. For this purpose, the holding element is preferably in a lower position so that it can be brought into engagement with the second locking element. In an upper position, however, the holding element can preferably not be locked with the second locking element. The locking, i.e. the movement of the holding element between the locking and unlocking positions, can be carried out manually or by actuator (e.g. via at least one hydraulic cylinder or hydraulic motor).

[0033] The locking mechanism can be implemented in the form of a bayonet lock, whereby rotation of the retaining element causes its locking element to retract into a recess in the corresponding second locking element. In the locked position, the retaining element can no longer be adjusted along the longitudinal axis relative to the support arrangement. Such a lock can be released or established quickly and easily, which simplifies and accelerates the process of uncoupling the power transmission device from the undercarriage during assembly of the superstructure (or coupling before dismantling the superstructure).

[0034] In a further possible embodiment, the support assembly comprises at least one second connecting element, which can be locked with a third locking element in order to connect the support assembly to the superstructure in a rotationally rigid manner, wherein the support assembly comprises, in particular, at least three second connecting elements and the superstructure comprises at least three third locking elements. At least one third locking element is preferably adjustably mounted on the superstructure, in particular screwed, in order to compensate for manufacturing tolerances and to be able to align the third locking elements (e.g., on a rotary joint between the superstructure and undercarriage).

[0035] In a further possible embodiment, it is provided that the second connecting element has a centering link which is designed to center the upper carriage relative to the support arrangement or to the undercarriage when establishing the connection between the upper carriage and the support arrangement by interacting with a corresponding link of the third locking element.

[0036] This ensures that the uppercarriage is automatically and precisely positioned relative to the undercarriage when the two are brought together. The centering linkage can be equipped with appropriately beveled surfaces. Pre-positioning of the uppercarriage can be achieved using the coupling device.

[0037] In a further possible embodiment, it is provided that the second connecting element and the third locking element form a quick coupling which is designed to carry out the locking and unlocking between the carrier arrangement and the superstructure regularly and quickly and easily.

[0038] The third locking element can preferably comprise a locking bolt that can be locked in at least two positions by means of a second locking means, which can be retracted into the second connecting element and locked thereto. The second connecting element can have a corresponding receptacle for this purpose, which can in particular be surrounded by the aforementioned centering slot. The locking between the locking bolt and the second connecting element takes place in particular by rotation of the locking bolt about its longitudinal axis. The locking, i.e. the movement of the locking bolt between the locking and unlocking positions, can take place manually or by actuator (e.g. via at least one hydraulic cylinder or hydraulic motor).

[0039] Preferably, the second connecting element further comprises a pre-tensioning link which interacts with the locking bolt in such a way that, when the locking bolt rotates about its longitudinal axis, a relative movement occurs between the second connecting element and the third locking element along the longitudinal axis of the locking bolt and these are clamped against each other, in particular via a spring element.

[0040] Two defined positions can be provided in which the locking bolt can be locked. For example, the locking bolt can have corresponding recesses into which a projection or pin of the second locking means engages.

[0041] In another possible embodiment, the carrier assembly comprises a driver that interacts with a slip ring assembly of the coupling device and transmits a rotational movement of the carrier assembly to a slip ring transmitter of the slip ring assembly. The driver can be connected to a bracket of the carrier assembly.

[0042] In a further possible embodiment, it is provided that the first shaft and / or the second shaft comprise a cardan shaft. The first shaft and / or the second shaft can comprise a plurality of cardan shafts which are connected to one another in an articulated manner, e.g. via cardan joints. The first shaft can comprise a vertical shaft and an angular gear, such that the first shaft can be guided to the power transmission means from below, in particular substantially parallel to the uppercarriage rotation axis. The first shaft is guided through the rotary union between the undercarriage and uppercarriage via the vertical shaft. The support arrangement is preferably seated on an upper side of the undercarriage.

[0043] In a further possible embodiment, the mechanical interface that releasably connects the power transmission means to the second shaft is or comprises a quick-action coupling. This allows the second shaft to be quickly and easily detached from or connected to the power transmission means, which simplifies and accelerates the assembly and disassembly of the superstructure. The quick-action coupling can preferably comprise a first quick-action coupling part with a profiled pin and a second quick-action coupling part with a receptacle profiled complementarily to the pin, which are plugged onto or into one another and can thus be releasably connected to one another in a force-fitting and / or form-fitting manner. Optionally, the connection can be reversibly locked by means of a locking means, e.g. a bolt or cotter pin.For example, said pin may represent the end of a rotatable shaft of the power transmission means and the receptacle may represent the end of the second shaft facing the support arrangement (or vice versa).

[0044] In a further possible embodiment, the upper carriage comprises a holding device to which the second shaft can be releasably connected in a transport position when separated from the power transmission means. If the upper carriage is removed from the undercarriage and the second shaft is thus separated from the power transmission means, the latter can be secured or held by the holding device. Preferably, the connection between the holding device and the second shaft also forms a quick-action coupling as described above. The holding device can be mounted on a support having one or more third locking elements.

[0045] In another possible embodiment, the superstructure is provided without a drive motor (single-engine operation with the superstructure supplied from the undercarriage). Alternatively or additionally, the superstructure can comprise at least one consumer (e.g., a pump distribution gear), with all consumers of the superstructure being driven directly or indirectly via the second shaft.

[0046] In a further possible embodiment, the work machine is designed as a mobile crane, with the undercarriage comprising a wheeled chassis and the superstructure comprising a boom, in particular a telescopic boom. The superstructure can be detached from the undercarriage via the coupling device and transported separately, with the undercarriage preferably being movable independently without the superstructure. The undercarriage preferably has an undercarriage operator's cab, via which the undercarriage can be moved in road traffic without an attached superstructure. The superstructure can have an superstructure ballast and / or an superstructure operator's cab.

[0047] In principle, the reverse variant would also be conceivable, i.e., the power transmission element is rotationally rigid or immovably connected to the superstructure in the transport state and is detachably connected or connectable to the first shaft via a mechanical interface, in particular a quick-release coupling as described above. In this case, the power transmission element could remain permanently connected to the superstructure, and only the mechanical connection to the first shaft would need to be established when mounting the superstructure on the undercarriage.

[0048] The present invention further relates to a drive system for the work machine according to the invention. The drive system comprises a motor, a first shaft mechanically driven by the motor, a second shaft, and a support assembly with a power transmission means that is detachably connected to the second shaft via a mechanical interface and connects the second shaft to the first shaft, as described above. The support assembly has the first and second connecting elements, as described above. This obviously results in the same properties and advantages as for the work machine according to the invention, so a repeated description is omitted.In particular, the drive system can be designed according to any of the previously described embodiments or any combination thereof, as long as the said embodiments relate to the components of the drive system (motor, first shaft, second shaft, power transmission means, carrier arrangement, first and second connecting elements, etc.).

[0049] In transport mode, the support assembly is separated from the superstructure and connected to the undercarriage. In working mode, the support assembly is firmly connected to the superstructure and separated from the undercarriage. The support assembly rotates with the superstructure and is, in particular, free from the undercarriage and can be rotated as desired through 360°. In both transport mode and working mode, the power transmission means is thus in the released state via the other connection, i.e. in particular (apart from an intermediate step during assembly or disassembly), neither in working mode nor in transport mode are both connections to the undercarriage and superstructure active or established at the same time.

[0050] The present invention further relates to a method for connecting the superstructure and undercarriage of a mobile work machine according to the invention. Initially, the undercarriage and the superstructure are provided as separate transport units, with the power transmission means being rotationally rigidly or immovably connected to the undercarriage (first connection) via the at least one first connecting element and thus secured against unintentional movement. Preferably, the power transmission means is separated from the drive train of the mobile work machine via a coupling.

[0051] The uppercarriage and undercarriage are then brought together, with the uppercarriage being placed on the undercarriage in a rotatable manner via the coupling device, e.g., using an auxiliary crane. The uppercarriage is pre-positioned, in particular, by connecting the undercarriage and uppercarriage at the coupling device. The rotary connection of the coupling device can preferably be established using a quick-coupling system (“Quick Connection”), which in particular involves inserting several bolts.

[0052] The uppercarriage must now be coupled to the power transmission system so that they can be rotated together relative to the undercarriage. To this end, a rotationally rigid or immobile connection (second connection) is established between the power transmission system and the uppercarriage via at least one second connecting element. In this state, the power transmission system is coupled to the undercarriage via the first connection and to the uppercarriage via the second connection.

[0053] Subsequently, the first connection, i.e., the rotationally rigid connection between the power transmission means and the undercarriage, is released via the at least one first connecting element, so that the power transmission means can now rotate freely together with the uppercarriage relative to the undercarriage without the support assembly contacting the undercarriage. In particular, the connection between the power transmission means and the first shaft, and possibly between a driver and the rotary union, remains.

[0054] The disassembly of the uppercarriage from the undercarriage is carried out in reverse order.

[0055] Further features, details, and advantages of the invention will become apparent from the following exemplary embodiments explained with reference to the figures. They show: Fig. 1: a side view of the mobile work machine according to the invention according to an embodiment; Fig. 2: a perspective view of an embodiment of the power transmission means on the undercarriage in the working state; Fig. 3: a perspective view of the power transmission on the undercarriage in transport condition; Fig. 4: a perspective view of the power transmission means; Fig. 5: a perspective view of the superstructure in transport condition; Fig. 6-7: perspective views of a holding means of the carrier arrangement in the unlocked and locked state; Fig. 8-9: Sectional views of a second connecting element and the third associated locking element in the unlocked and locked states; and Fig. 10: a sectional view through the rotary connection of the coupling device according to an embodiment.

[0056] In the Fig. Figure 1 shows a side view of an embodiment of the work machine 10 according to the invention in the form of a mobile crane. Although the following description of the embodiments is based on this mobile crane, the drive system according to the invention is not limited to such a crane, but can be used in various work machines with undercarriages and superstructures.

[0057] The mobile crane 10 comprises an undercarriage 12 with several wheel axles and an undercarriage driver's cabin 15 as well as an uppercarriage 14 mounted on the undercarriage 12 via a coupling device 20 about a vertical uppercarriage rotation axis, with a boom 16 that can be tilted up and down about a horizontal pivot axis. The uppercarriage 14 can, as shown in the Fig. 1, also have a superstructure driver's cab 17. In this embodiment, the boom 16 is designed as a telescopic boom, which can be pivoted about the horizontal pivot axis by means of one or more luffing cylinders 18.

[0058] The coupling device 20 comprises a slewing ring 23 in the form of a large roller bearing, as is common with larger mobile cranes. The coupling device 20 is designed such that the uppercarriage 14 can be removed from the undercarriage 12. This allows the uppercarriage 14, with its considerable dead weight, to be transported to the site as a separate transport unit independent of the undercarriage 12. The undercarriage 12 can be moved on public roads without the uppercarriage 14, whereby the permissible axle loads are maintained due to the reduced weight. To enable the regular attachment and detachment of the uppercarriage 14, the coupling device 20 is specially designed for this purpose and preferably comprises a special quick-coupling device 26, which enables quick and easy assembly and disassembly of the uppercarriage 14.

[0059] In the Fig. 10 shows a section through a possible embodiment of the rotary joint 23. In this variant, the quick-coupling device 26 is based on a tongue and groove connection. The rotary joint 23 comprises a first quick-coupling part 21, which is connected, in particular screwed, to the undercarriage 12, and a second quick-coupling part 22, which is connected, in particular screwed, to the superstructure 14. In the embodiment shown, the first quick-coupling part 21 has an annular circumferential groove, while the second quick-coupling part 22 has a corresponding annular circumferential web which, when connected, lies within the groove. Both quick-coupling parts 21, 22 have a plurality of bolt receptacles distributed around the circumference, through which corresponding locking bolts 24 can be inserted to releasably lock the undercarriage 12 and superstructure 14.

[0060] In the Fig. In the embodiment shown in Figure 10, the second quick-coupling part 22 comprises the aforementioned large roller bearing, which can alternatively be installed in the first quick-coupling part 21. Conversely, the first quick-coupling part 21 can also have the web and the second quick-coupling part 22 can have the groove, or the first quick-coupling part 21 could alternatively be connected to the uppercarriage 14 and the second quick-coupling part 22 to the undercarriage 12.

[0061] The undercarriage 12 has a motor that drives one or more consumers of the uppercarriage 14, such as a pump distribution gear for supplying the luffing cylinder 18 and other hydraulic consumers. This is done via a mechanical drive system that extends from the undercarriage 12 through the slewing ring 23 between the undercarriage and uppercarriage 12, 14 into the uppercarriage 14. The drive system comprises a first shaft 51 in the undercarriage 12 and a second shaft 52 in the uppercarriage 14, which are mechanically coupled to one another by a power transmission means 30. The undercarriage motor drives the first shaft 51 in a rotational manner, wherein the rotational movement is transmitted to the second shaft 52 via the power transmission means 30. The two shafts 51, 52 are designed as cardan shafts and can comprise several individual shafts that are articulated to one another. The first shaft 51 is vertical, i.e.parallel to the superstructure rotation axis, guided through the slewing ring 23 in the direction of the superstructure 14. For this purpose, the first shaft 51 can comprise a main shaft and an angular gear arranged in the undercarriage 12 in order to deflect the shaft 51 in the direction of the superstructure 14.

[0062] To disassemble the superstructure 14, the mechanical drive system must be separated or uncoupled. To ensure this can be done quickly and easily, the power transmission means 30 that couples the first and second shafts 51, 52 has a mechanical interface 40 at which the uncoupling takes place.

[0063] In the Fig. Figure 2 shows a preferred embodiment of the drive system according to the invention or of the power transmission means 30 in a perspective view with a view of the rotary joint 23 between the undercarriage and the upper carriage 12, 14. Parts of the upper carriage 14 are hidden in order to reveal the power transmission means 30 located within the rotary joint 23. In this embodiment, the latter is designed as an angular gear 30, which is mechanically connected at the bottom to the first shaft 51 and laterally via the aforementioned mechanical interface 40 to the second shaft 52. The shafts 51, 52 can have universal joints, as shown in the Fig. 2 and Fig. 3. In the illustrated embodiment, the mechanical interface 40 is designed as a quick-coupling mechanism to enable the second shaft 52 to be quickly and easily separated from or coupled to the angular gear 30.

[0064] The Fig. Figure 3 shows the bevel gear 30 with the upper carriage 14 removed in the transport position, with parts of the slewing ring 23 connected to the undercarriage 12 hidden. The bevel gear 30 is held by a support assembly 32, which, in the transport position, is rotationally rigidly and immovably connected to the undercarriage 12 via first connecting elements 60.

[0065] As in the Fig. 3, the undercarriage 12 has a passage 13 below the support arrangement 32 through which the first shaft 51 is guided outwards to the angular gear 30.

[0066] In the illustrated embodiment, the support assembly 32 comprises a bracket 34, which comprises the first connecting elements 60. The angular gear 30 can be connected to a holder 35, which is connected to the bracket 34 via an arrangement of damping elements 36. The illustrated embodiment has a symmetrical arrangement of four damping elements 36, which can be designed, for example, as elastomer bearings, as shown in Fig. 4. An arrangement of springs (e.g., disc springs) is also conceivable. The elastic mounting of the angular gear 30 allows for the compensation of relative movements between the undercarriage 12 and the uppercarriage 14.

[0067] The carrier arrangement 32 may include a driver 38 (see Fig. 3 and Fig. 4), which can be connected, for example, to the bracket 34 or the holder 35. In the operating state, a rotary movement of the support assembly 32 and thus of the superstructure 14 can be transmitted via the driver 38 to a slip ring transmitter of a slip ring arrangement arranged in the rotary feedthrough. The slip ring arrangement can surround the first shaft 51 in a ring-shaped manner.

[0068] The Fig. 4 shows only the support assembly 32 with the bevel gear 30. Here, the bevel gear-side part of the quick-coupling forming the mechanical interface 40 can be seen, which forms a first quick-coupling part. The end of the second shaft 52 facing the bevel gear 30 has a matching second quick-coupling part. This allows the second shaft 52 to be quickly and easily separated from the bevel gear 30 for disassembly of the uppercarriage 14 or connected to it for assembly of the uppercarriage 14. The first shaft 51 can also be connected to the bevel gear 30 via such a quick-coupling or, alternatively, be permanently connected to it. The bracket 34 can include a receptacle 39 for an oil cooler. As a result, the support assembly 32 forms a thermally self-sufficient unit, and no fluids need to be supplied or removed.

[0069] The dismantled superstructure 14 is shown in a perspective view in the Fig. 5. In this embodiment, the second shaft 52 is mounted in a holding device 54. This can have a corresponding first quick-coupling part, such as the bevel gear 30, so that the second quick-coupling part of the second shaft 52 can be connected to it in a transport position. This ensures that the second shaft 52 is held securely in the transport position during transport of the superstructure 14.

[0070] In the working position, in which the uppercarriage 14 is connected to the undercarriage 12, the angular gear 30 is rotationally rigidly coupled to the uppercarriage 14, so that both can rotate about a common axis of rotation (which corresponds in particular to the uppercarriage rotation axis). Since the first connection between the support arrangement 32 and the undercarriage 12 is not rotatable but rotationally rigid, this first connection must be released for the working state. Beforehand, the uppercarriage 14 must be rotationally rigidly coupled to the power transmission means 30 via a second connection, which is established via corresponding second connecting elements 80 of the support arrangement 32. As a result, the drive of the uppercarriage consumers in the working state can take place via the mechanical drive system in any rotational position of the uppercarriage 14.In the transport state, in which the upper carriage 14 is removed from the undercarriage 12, the angular gear 30 is connected to the undercarriage 12 in a rotationally fixed manner so that it does not move unintentionally, for example during road travel.

[0071] In the embodiment shown, the support assembly 32 has three first connecting elements 60, which form a stable tripod support for the support assembly 32. Alternatively, fewer or more than three first connecting elements 60 may be present. Fig. 6-7 one of these first connecting elements 60 is shown in perspective in two different positions: the Fig. 6 shows the position of the first connecting element 60 in the working state, while the Fig. 7 shows its position in transport condition.

[0072] The first connecting element 60 comprises a rod-shaped holding element 62, which is displaceably mounted in a receptacle 61 of the bracket 34 and can be locked in at least the two positions shown by a first locking means 64 ( Fig. 6: upper position, Fig. 7: lower position). For this purpose, the first locking means 64 can comprise a possibly spring-loaded securing bolt, which in the upper position of the holding element 62 (cf. Fig. 6) into a corresponding lower recess or bore 63b and in the lower position of the holding element 62 (cf. Fig. 7) engages a corresponding upper recess or bore 63a of the retaining element 62 and secures the retaining element 62 against displacement along its longitudinal axis and / or against rotation about its longitudinal axis. The first locking means 64 can be designed as a sash lock.

[0073] At its lower end facing the undercarriage 12, the holding element 62 has a first locking element 66, which is designed to cooperate in a locking position with a second locking element 70 mounted on the undercarriage 12 and to lock the holding element 62 therein. The second locking element 70 can, as shown in the Fig. 6, comprise a holding plate 72 connected, in particular screwed, to the undercarriage 12, on which an upper holding part 74 is mounted. The latter has a recess 75 open towards the holding element 62, into which the first locking element 66 of the holding element 62 fits when the latter is in its lower position (cf. Fig. 7) can be retracted by rotating it around its longitudinal axis. The holding element 62 is then in its locking position. If all holding elements 62 are locked in their respective second locking elements 70, the rotationally rigid first connection to the undercarriage 12 is established (see Fig. 3). The first locking means 64 secures the holding element 62 against unintentional unscrewing of the first locking element 66 from the recess 75.

[0074] The upper holding part 74 can be mounted on the lower holding plate 72 via at least one spring. This can be designed as a disc spring (the embodiment of the Fig. 6 shows an arrangement with two disc springs) and prevents vertical movement of the carrier assembly 32 during transport.

[0075] The holding element 62 can have a pin 65 at its end facing the undercarriage 12 in the region of the first locking element 66, which pin 65 lies in a bore or in a corresponding recess 73 of the lower holding plate 72 in the lower position of the holding element 62 and thereby centers the holding element 62 and secures it against lateral slipping by means of a positive locking.

[0076] In the Fig. In the embodiment shown in Figures 6-7, the retaining element 62 comprises a bayonet screw mounted in a retaining bolt, and the first locking element 66 is formed as a substantially semicircular plate as part of the bayonet screw. By turning the retaining bolt with the bayonet screw, the plate 66 slides into the recess 75 between the retaining plate 72 and the upper retaining part 74. The retaining bolt can have an actuating section (for example, in the form of a hexagon) at its end facing away from the plate 66, so that it can be rotated with the aid of a tool.

[0077] The holding element 62 is preferably designed to be variable in length in order to compensate for manufacturing tolerances and to provide the necessary distance in the working state. In the embodiment of the Fig. 6-7, the bayonet screw is secured in the retaining bolt 62 via a lock nut 67. By loosening the lock nut 67, the bayonet screw can be unscrewed from the retaining bolt or screwed further in to change the height or length of the entire retaining element 62.

[0078] The rotationally rigid connection between the support arrangement 32 and the superstructure 14 is effected via second connecting elements 80, which can also be arranged on the console 34 (cf. Fig. 4). In the illustrated embodiment, three second connecting elements 80 are present, although fewer or more than three second connecting elements 80 are also conceivable. Accordingly, three third locking elements 90 are located on the upper carriage 14, which can be reversibly connected to the second connecting elements 80 to form the second connection.

[0079] The second connecting elements 80 have a receptacle and in the embodiment shown comprise the Fig. 8-9 further comprise a centering link 82 with outwardly beveled surfaces on the upper side for automatically positioning the upper carriage 14 upon connection to the support assembly 32, after it has already been pre-positioned by connecting the rotary connection parts 21, 22. The third locking elements 90 have a complementary link on the underside, which interacts with the respective centering link 82.

[0080] The Fig. Figure 8 shows a sectional view of a second connecting element 80 with an associated third locking element 90 placed thereon, whereby these are not yet locked together, while the Fig. 9 shows the locked state. The third locking element 90 comprises a sleeve 96, which has the aforementioned slotted guide on its underside and in which a locking bolt 92 is slidably received. In an upper position (cf. Fig. 8), the lower end of the locking bolt 92 does not protrude into the receptacle of the second connecting element 80, and the connection is not yet established. The locking bolt 92 is secured in the upper position by a second locking means 94, which can be designed as a sash. For this purpose, the locking bolt 92 can have a lower recess or bore 93b into which a locking pin of the second locking means 94 engages. The latter can be spring-loaded. The sleeve 96 can also have a receptacle for a spring 98 (e.g., a disc spring), the function of which is described below.

[0081] To establish the second connection, the locking bolt 92 (after releasing the second locking means 94) is inserted into the receptacle of the second connecting element 80 and secured in a locking position by rotation about its longitudinal axis (cf. Fig. 9). For this purpose, the locking bolt 92 can have one or more locking pins 95 at its end facing the second connecting element 80, which positively block withdrawal of the locking bolt 92 in the locking position.

[0082] The second connecting element 80 preferably has a pre-tensioning link 84 on its lower region, which is facing away from the centering link 82 (cf. Fig. 8) with guide surfaces which are ramp-like and bevelled in the circumferential direction around the receptacle for the locking bolt 92, along which the locking pin(s) 95 are guided from below by rotation of the locking bolt 92 until they laterally abut a stop which defines the locking position of the locking bolt 92. The locking bolt 92 can also be secured against unscrewing in the locking position by the second locking means 94, which for this purpose engages in a corresponding upper recess or bore 93a of the locking bolt 92 (cf. Fig. 9).

[0083] Due to the ramp shape of the lower pre-tensioning link 84, a rotation of the locking bolt 92 about its longitudinal axis (for this purpose, the locking bolt 92 can be rotated as shown in the Fig. 8-9, for example, a hexagon for attaching a corresponding tool) a relative vertical movement between the second connecting element 80 and the third locking element 90 counter to the force generated by the spring 98, so that they are clamped against each other. The spring 98 presses the locked locking bolt 92 from below against the preloading guide 84, which forms a stop and secures the locking bolt 92.

[0084] In the embodiment of the Fig. 8-9, each second connecting element 80 comprises a link element 81, which has the described centering and preloading links 82, 84 and is connected, in particular screwed, to the bracket 34. Alternatively, the second connecting elements 80 or the centering and preloading links 82, 84 could be formed directly in the bracket 34.

[0085] As in the Fig. 5, two third locking elements 90 can be arranged on a first support 56, which is preferably adjustably screwed to the upper carriage 14 in order to compensate for manufacturing tolerances and to be able to align the third locking elements 90, for example, on the rotary joint 23. A further third locking element 90 can be arranged on a second support 58, which can also be adjustable. In the embodiment of Fig. 5, the holding device 54 for the second shaft 52 is located on the second carrier 56.

[0086] In order to bring the mobile crane 10 into working condition after the separate transport of the undercarriage and uppercarriage 12, 14, the uppercarriage 14 must be reconnected to the undercarriage 12. For this purpose, the uppercarriage 14 is lowered over the undercarriage 12, e.g., using an auxiliary crane. The uppercarriage 14 is pre-centered and bolted by the slewing ring mount of the quick-coupling device 26 of the coupling device 20 ("Quick Connection"). Precise positioning is achieved through the interaction of the centering links 82 and sleeves 96 when establishing the second connection. To lock the second connection, the second locking means 94 are opened and the locking bolts 92 are turned. A stop on the centering link 82 or on the receptacle of the second connecting elements 80 positions the locking bolts 92 and the second locking means 94 can now be inserted into the upper recesses 93a, which secures the locking bolts 92 against loosening.The now tensioned disc springs 98 hold the locking bolts 92 in position (see . Fig. 9).

[0087] In order to release the carrier assembly 32 from the undercarriage 12, the first locking means 64 are opened. Now the holding elements 62 can be rotated (in the illustrated embodiment, the Fig. 6-7 by 180°, although a rotation of 90° or another angle could also be provided, for example) and raised. Through the lower recesses 63b, the holding elements 62 can be fixed in the upper position via the first locking means 64 (cf. Fig.6). The support assembly 32 is now only connected to the undercarriage 12 via the first shaft 51 and can rotate with the superstructure 14. By attaching the driver 38 to the support assembly 32, it is sufficient to adjust it once (unlike if it were fixed to the superstructure 14). The second shaft 52 can then be removed from its transport bracket or holding device 54 and connected to the angular gear 30 via the quick-release coupling 40. List of reference symbols: 10 work machine (mobile crane) 12 undercarriage 13 Implementation 14 superstructure 15 Undercarriage driver's cab 16 booms 17 Superstructure driver's cab 18 rocker cylinders 20 Coupling device 21 First slewing ring part 22 Second slewing ring part 23 Second slewing ring 24 locking bolts 26 Quick coupling device 30 Power transmission devices (angle gears) 32 carrier arrangement 34 Console 35 holders 36 Damping element 38 drivers 39 Oil cooler mount 40 Mechanical interface (quick coupling) 51 First Wave 52 Second Wave 54 Holding device 56 First Carrier 58 Second carrier 60 First connecting element 61 recording 62 Holding element 63a Upper recess 63b Lower recess 64 First locking device 65 cones 66 First locking element 67 Lock nut 70 Second locking element 72 retaining plate 73 Recess 74 Upper holding part 75 recess 76 spring 80 Second connecting element 81 backdrop element 82 Centering backdrop 84 Opening credits backdrop 90 Third locking element 92 locking bolts 93a Upper recess 93b Lower recess 94 Second locking device 95 locking pin 96 sleeve 98 spring

Claims

[1] Mobile work machine (10), in particular a mobile crane, comprising a movable undercarriage (12), an uppercarriage (14) which is mounted on the undercarriage (12) so as to be rotatable about a superstructure rotation axis and which is detachably connected to the undercarriage (12) via a coupling device (20), and a mechanical power transmission means (30), wherein the undercarriage (12) comprises a motor and a first shaft (51) which is mechanically driven by the motor and which is mechanically connected to a second shaft (52) of the superstructure (14) via the power transmission means (30), characterized bya support arrangement (32) on which the power transmission means (30) is mounted and which comprises first and second connecting elements (60, 80) via which the power transmission means (30) can be connected in a rotationally rigid manner to the undercarriage (12) in a transport state in which the upper carriage (14) is separated from the undercarriage (12) and in a rotationally rigid manner to the upper carriage (14) in a working state in which the upper carriage (14) is rotatably mounted on the undercarriage (12), wherein the power transmission means (30) is detachably connected to the second shaft (52) via a mechanical interface (40) in the working state. [2] Mobile work machine (10) according to claim 1, wherein the power transmission means (30) is or comprises an angular gear, which preferably comprises a first mechanical interface and a second mechanical interface (40), via which the angular gear (30) is mechanically releasably connected to the first and second shafts (51, 52) in the working state. [3] Mobile work machine (10) according to one of the preceding claims, wherein the coupling device (20) comprises a rotary joint (23), in particular designed as a rolling bearing, which preferably comprises a first rotary joint part (21) connected to the undercarriage (12) and a second rotary joint part (22) connected to the superstructure (14), which are detachably connected to one another via a quick-coupling device (26). [4] Mobile work machine (10) according to the preceding claim, wherein the power transmission means (30) is arranged within the rotary joint (23), wherein the upper carriage (14) in the working state is preferably only rotatably connected to the undercarriage (12) via the rotary joint (23) of the coupling device (20). [5] Mobile work machine (10) according to one of the preceding claims, wherein the support arrangement (32) comprises a bracket (34) which has the first and second connecting elements (60, 80), wherein the force transmission means (30) is preferably connected to the bracket (34) via at least one damping element (36) of the support arrangement (32), in particular via an arrangement of a plurality of damping elements (36) symmetrical to a rotational axis of the force transmission means (30). [6] Mobile work machine (10) according to one of the preceding claims, wherein the carrier arrangement (32) comprises at least one first connecting element (60) with a holding element (62) which can be locked in at least two positions via a first locking means (64), wherein the holding element (62) comprises a first locking element (66) which can be brought into engagement with a second locking element (70) arranged on the undercarriage (12) in order to connect the carrier arrangement (32) to the undercarriage (12) in a rotationally rigid manner, wherein the first connecting element (60) and the second locking element (70) preferably form a quick coupling, wherein the carrier arrangement (32) in particular comprises at least three first connecting elements (60) and the undercarriage (12) at least three second locking elements (70). [7] Mobile work machine (10) according to the preceding claim, wherein the holding element (62) is adjustable relative to the force transmission means (30) along a longitudinal axis running in particular parallel to the superstructure rotation axis and can be locked in at least two different longitudinal positions via the first locking means (64), wherein preferably the holding element (62) is movable by rotation about its longitudinal axis between a locking position in which the holding element (62) and the second locking element (70) are locked together, and an unlocking position in which a movement of the holding element (62) in the longitudinal direction is released. [8] Mobile work machine (10) according to one of the preceding claims, wherein the carrier arrangement (32) comprises at least one second connecting element (80) which can be locked with a third locking element (90) which is mounted in particular adjustably on the superstructure (14) in order to connect the carrier arrangement (32) to the superstructure (14) in a rotationally rigid manner, wherein the carrier arrangement (32) in particular comprises at least three second connecting elements (80) and the superstructure (14) comprises at least three third locking elements (90). [9] Mobile work machine (10) according to the preceding claim, wherein the second connecting element (80) has a centering link (82) which is designed to center the upper carriage (14) relative to the undercarriage (12) when establishing the connection between the upper carriage (14) and the support arrangement (32) by interacting with a corresponding link of the third locking element (90). [10] Mobile work machine (10) according to claim 8 or 9, wherein the second connecting element (80) and the third locking element (90) form a quick coupling, wherein the third locking element (90) preferably comprises a locking bolt (92) which can be locked in at least two positions by means of a second locking means (94), which can be inserted into the second connecting element (80) and can be locked to the second connecting element (80), in particular by rotation about its longitudinal axis. [11] Mobile work machine (10) according to one of the preceding claims, wherein the first shaft (51) and / or the second shaft (52) comprises a cardan shaft and / or wherein the first shaft (51) comprises a vertical shaft and an angular gear. [12] Mobile work machine (10) according to one of the preceding claims, wherein the mechanical interface (40) which releasably connects the power transmission means (30) to the second shaft (52) is or comprises a quick coupling, wherein the quick coupling (40) preferably comprises a first quick coupling part (41) with a profiled pin and a second quick coupling part (42) with a receptacle profiled complementarily to the pin, which can be releasably connected to one another in a force-fitting and / or form-fitting manner. [13] Mobile work machine (10) according to one of the preceding claims, wherein the superstructure (14) has no drive motor and / or wherein the superstructure (14) comprises at least one consumer and all consumers of the superstructure (14) are driven directly or indirectly via the second shaft (52). [14] Drive system for a mobile work machine (10) according to one of the preceding claims, comprising an engine, a first shaft (51) mechanically drivable by the engine, a second shaft (52) and a support arrangement (32) with a power transmission means (30) which is detachably connected to the second shaft (52) via a mechanical interface (40) and connects the second shaft (52) to the first shaft (51), wherein the support arrangement (32) comprises first and second connecting elements (60, 80) via which the power transmission means (30) can be connected in a rotationally rigid manner to the undercarriage (12) in a transport state in which the upper carriage (14) is separated from the undercarriage (12) and in a working state in which the upper carriage (14) is rotatably mounted on the undercarriage (12), can be connected in a rotationally rigid manner to the upper carriage (14). [15] Method for connecting the superstructure (14) and the undercarriage (12) of a mobile work machine (10) according to one of claims 1 to 13, comprising the following steps: - providing the undercarriage (12) and the superstructure (14) as separate transport units, wherein the power transmission means (30) is rotationally rigidly connected to the undercarriage (12) via the at least one first connecting element (60); - Bringing together the upper carriage (14) and the undercarriage (12), wherein the upper carriage (14) is placed on the undercarriage (12) in a rotatable manner via the coupling device (20); - establishing a rotationally rigid connection between the power transmission means (30) and the superstructure (14) via the at least one second connecting element (80); and - releasing the rotationally rigid connection between the power transmission means (30) and the undercarriage (12) via the at least one first connecting element (60), so that the power transmission means (30) can rotate freely together with the upper carriage (12) relative to the undercarriage (12) without the support arrangement (32) contacting the undercarriage (12).

Images